Automatic back gauge spacer



Nov. l, 1949 F. w. sEYBoLD 2,487,031

AUTOMATIC BACK GAUGE SPACER Filed Jan. 15, 194e 11' sneetssneet 1 Nov. l, 1949 F. w. sEYBoLD AUTOMATIC BACK GAUGE SPACER 11 Sheets-Sheet 2 Filed Jan. l5. 1948 INVENTOR. vF/ae-DERvc/f w. sfrsow. 9 BY Nov. 1, 1949 F. w. sEYBoLD 2,487,031

AUTOMATIC BACK GAUGE SPACER l1 Sheets-Sheet 3 Filed Jan. 15, 1948 NvEN'roR .A

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BY UMYMI ATTORNEYS.

Nov. l, 1949 F. w. sEYBoLD AUTOMATIC BACK GAUGE SPACER Filed Jan. 15'. 194s 11 Sheets-Sheet 4 ATTORNEYS.

Nov. 1, 1949 Filed Jan. 15, 1948 F, W. SEYBOLD AUTOMATIC BACK GAUGE SPACER 11 Sheets-Sheet 5 INVENTOR.

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Nov. 1, 1949 F. w. sEYBoLD 2,487,031

AUTOMATIC BACK GAUGE SPACER Fild Jan. 15, 1948 11 Sheets-Sheet 6 FIG. B.

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Nov. l, 1949 F. w. sEYBoLD AUTOMATIC BACK GAUGE SPACER 11 Sheets-Sheet 7 Filed Jan. l5, 1948 V/EW /N PERSPECTIVE 0N l//VE F IG. 3 SHOW/N6 FIA/651? P UPPER SPL/NED SHAFT /N OPERATIVE POS/T/ON.

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ATTORNEYS Nov. 1, 1949 F. w. sEYBoLD AUTOMATIC BACK GAUGE SPACER Filed Jan. l5, 1948 11 Sheets-Sheet 8 .Ff/Vai g BY M ATTORNEYS.

Nov. l, 1949 F. w. sEYBoLD AUTOMATIC BACK GAUGE SPACER ll Sheets-Sheet 9 Filed Jan. 15, 1948 INVENTOR. FEEDER/C7( l/V. SEYBOZD.

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Nov. l, 1949 F. w. sEYBoLD AUTOMATIC BACK GAUGE SPACER l1 Sheets-Sheet 10 Filed Jan. l5, 1948 m. m Rw O T s mw ww -m n P. F Y B AT1-0R Evs.

Nov. l, 1949 F. w. sEYBoLD AUTOMATIC BACK GAUGE SPACER 11 Shee'ts-Sheet 11 Filed Jan. 15, 1948 .Emi O .Emi 0mm .Emi OO@ .SEK @NNI .Em .m OO@ I.

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W GES/BOLD TTORA/EVS Patented Nov. l, 1949 2,487,031 AUTOMATIC BACK GAUGE SPACER Frederick W.

to E. P. Lawson Seybold, Westfield, N. J., assignor Co., Inc.,

New York, N. Y., a

corporation oi' New York Application January 15, 1948, Serial No. 2,347

40 Claims.

down. it will cut oi! an exactly dimensioned section of the pile.

In operating paper cutters of this type, therefore, it frequently becomes necessary to adjust the back gauge many times for different cuts which are to be made. Even if a plurality of regular cuts is to be made from a single pile, the back gauge must be moved up each time in order to ensure that the edges are perfectly squared so that the exact cut may be made.

The object of my invention is the provision of a novel automatic back gauge spacing mechanism which will adjust the back gauge at successive individually predetermined intervals after successive cuts.

By the use of my invention, therefore, the operator need do nothing more than place the initial pile of paper on the machine against the back gauge and then operate the paper cutter so that the knife moves up and down a desired number of times to cut the desired number of piles.

The back gauge automatic spacing mechanism automatically moves the back gauge the proper distance at the end of each cut and before the next cut is started.

Automatic operation or spacing of the back gauge is already known as shown in the prior Patent No. 2,053,499.

My invention is directed specifically to simplied presetting mechanism which will operate repetitively through the same cycle until the presetting mechanism has been readJusted.

My invention is also directed to novel operating means for the back gauge which will bring the back gauge into movement promptly at the completion of a cutting cycle, move the back gauge rapidly to the next selected position and then decelerate the back gauge gradually to its next adjusted position, the gradual deceleration of the back gauge preventing overshooting of the predetermined mark.

For presetting purposes. my invention includes revolving presetting bars located at the front of the machine. each provided with a plurality of grooves in which stop pins may be slidably adjusted longitudinally of the bars.

Preferably, I provide two such longitudinal bars at the front of the machine, each of the longitudinal revolving bars having ten equally spaced longitudinal grooves. The stop pins are longitudinally adjustable in each of tl grooves.

A stop member mounted on a. cable connected to the back gauge operating mechanism and movable along a line parallel to the bars successively engages the preset stop pins in the bars. When the stop member engages a stop pin, the back gauge adjusting mechanism is brought to a halt, and the back gauge is set for its next adjustment.

On the completion of a cut, the stop bars are rotated 11s of a revolution to bring the next groove in each bar into-line with lthe stop member. This pulls the stop pin out of engagement with the stop member. and the stop member is free to move simultaneously with the movement of the back gauge to a position where the stop member engages the next stop pin in the adjacent groove which has been rotated to stopping position, at which time the mechanism for operating the back gauge is again brought to a halt.

My invention is thus directed to novel stop members for controlling successive positions of the back gauge; novel indexing elements for moving stop members successively into position; and novel mechanical operating elements responsive to the operation of the knife to move the back gauge under the control of the stop members and the indexing elements in such a manner that the back gauge will always be accurately positioned.

Thus, an object of my invention is the provision ofnovel automatic back gauge stepping means for moving the back gauge to a number of predetermined positions.

Another object of my invention is the provision of novel revolving stop bars at the front of the machine by means of which all of the successive positions which the back gauge is to assume may be pre-set by the operator at the front of the machine.

Another object of my invention is the provision of novel indexing apparatus for controlling successive positions of the stop bars and hence successive positions of the back gauge.

Another object of my invention is the provision of mechanical operating means for moving my back gauge under the control of the stop bars and indexing elements so that the back gauge will move accurately to the predetermined position.

Another object of my invention is the provision of novel speed control means for the operating mechanism of my novel back gauge to cause the same to move the back gauge rapidly between intervals but to bring it to a,y slow stop so that it will not overshoot the predetermined setting.

The foregoing and many other objects of my invention will become apparent in the following description and drawings in which:

Figure 1 is a side view of a cutting knife embodying my novel spacer mechanism and the operating, indexing, and control elements thereof.

Figure 2 is a top view of the unit of Figure 1.

Figure 3 is a front view of the control or indexing elements for my novel spacer mechanism.

Figure 4 is an end view partly in cross-section taken on line 4-4 of Figure 1 looking in the direction of the arrows and showing the operating elements of my novel spacer mechanism.

Figure 5 is a cross-sectional view of the operating elementsV of my novel spacer mechanism taken on line 5-9 of Figure 4 looking in the direction of the arrows.

Figure 6 is an enlarged side view of the control and indexing elements of my novel spacer mechanism, the said view being an enlargement of the upper left portion of Figure 1.

Figure 7 is a cross-sectional view of a portion of the index and control elements of my novel spacer mechanism taken on line 1 1 of Figure 6 looking in the direction of the arrows.

Figure 8 is a View corresponding to that of Figure 6 showing another position of the index and control elements.

Figure 8A is a cross-sectional view through a portion of the index and control elements of my novel spacer mechanism taken on line 8A-8A of Figure 6 looking in the direction of the arrows.

Figure 9 `is a cross-sectional view through a portion of the index and control elements of my novel spacer mechanism taken on line 9-9 of Figure 8 looking in the direction of the arrows.

Figure 10 is a cross-sectional view through the main operating shaft of the operating elements of my novel spacer mechanism taken on line |L|0 of Figure 5 looking in the direction of the arrows.

Figure 11 is a perspective view partly in crosssection through the splined indexing shafts or bars of the control section of my novel spacing mechanism taken on line of Figure 3 looking in the direction of the arrows.

Figure 12 is an elevation partly in cross-section of the stop mounting for the control elements of Figure 11 taken on line |2-I2 of Figure 11 looking in the direction of the arrows.

Figure 13 is a cross-sectional view taken on line |3|0 of Figure 12 locking in the direction of the arrows.

Figure 14 is a cross-sectional view of the stopping element for cooperating with the stops on the splined shafts taken on line |4|4 of Figure 11 looking in the direction of the arrows.

Figure 15 is an expanded view in perspective of the operating elements of Figure 5.

Figure 16 is a schematic view in perspective showing the positions of the speed shifting levers.

Figure 17 is an expanded view in perspective of the indexing mechanism of Figure 8.

Figure 17a is a view in perspective of one of the indexing pins of Figure 17.

of Figure 17.

Figures 3, 6 to 9).

55 housings of the paper cutting machine.

Figure 19 (on Sheet '1) is a view in perspective of one of the stop pins.

Figure 20 is a graphic illustration of the operation of my invention.

5 In the following figures, the stop bars and their operation will be more clearly understood from Figures 3, 11 to 14 and 16; the indexing mechanism will be more clearly understood from Figures 1, 3, 6, 7, 8 and especially Figure 17; the

l0 operating elements including the speed shifting means will be more readily understood from Figures 1, 2, 4, 5 and especially Figures 15 and 16.

Reference is first made to Figures 3, 11 to 14, and 16.

15 The two stop bars 99 and |00 are spaed apart 5 their original position after all of the stops |25 on'the stop bar have been contacted. In other words, assuming that it takes thirty-seven knife strokes to completely cut up a given pile of paper and as there are ten splines |40 in each of the stop bars 99 and |00, each stop bar would have made 3.7 revolutions; in order thereafter to return the stop bars to their original position for making a first cut on a second pile of paper identical with the first pile of paper, it will be necessary to turn the stop bars 99 and |00 through an additional 1% of a revolution so that the first stop block |20 will be in line to stop the back gauge for the first knife stroke.

In order to accomplish this .3 additional revolution of the stop bars 99 and |00 at the completion of the thirty-seven cuts taken as an example, a series of cams and gearing is provided. The stop bars 99 and |00 which are provided with ten splines |40 each are each indexed 11e of a revolution after each knife stroke to bring the next stop |25 into its proper position to stop the back gauge. This indexing movement is accomplished as follows:

Stop bars 99 and |00 are rotatably mounted at the left end on the cone-shaped spindle |02 of adjustable screws |03 which can be locked in adjusted position by the knurled nuts |04. The screws |04 are mounted in threaded bores |05, |05 in the brackets |08 which are fastened to the On the right hand side, stop bars 99 and |00 are each mounted on a retractable cone sleeve ||0. Cone sleeves ||0 are hollow and fit over the shafts I ||l, the latter having a counterbore or recess ||2 60 to receive the compression spring I9.

Longitudinal slots ||4 diametrically opposite in each shaft receive the cylindrical ends of screws |20 which limits the movement of the conical sleeves ||0 to the left. A pin |2| passes perpendicularly through the sleeve ||0 near its left-hand end, said pin being used to register with a. slot |22 in each stop bar 99 and |00. Pin |2|,

therefore, is the driving member to rotate the stop bar 99 and |00.

0 A thrust bearing m which n mounted en the shaft takes the thrust which is caused by the compression spring ||3 bearing against this conical sleeve ||0 and the shaft I, said thrust being taken by the bracket |00. The conical screw |09 5 beine stumme permits the sainement rer 1st.

eral displacement of the stop bar 99 or |89 so that after a series of stops |25 (Figures 3, 11 to 14) have been setup on the bars 99 and |80 and it should be found desirable that the entire setup should be shifted either to the right or the left, this can be done by merely adjusting the screw |08 of each bar 99 and |00 and locking it in place thereafter by means of the lock nut I I4.

A cross head |42 is reciprocated by a roller |48 which is carried on a stud |44 mounted on the knife bar casting |45 (Figures 6 and 17). Roller |48 rides in channel |45 secured to cross-head |42. Cross head |42 ls urged in the upward direction by the compression spring |41 which fits loosely over the stationary shaft |48. n the cross head |42 is mounted the push bar |50 on the upper end of which is mounted the pawl |52 which may contact the pin on the pawl lever |49, said lever being fulcrummed on the upper shaft The additional pawl lever 4| is mounted on a. pin |39 on the pawl lever |49 so that when the cross head |42 makes its upward movement, the pawl |52 will contact the pin |5| and rock the pawl lever |49 in a counterclockwise direction. Then the pawl |4| which engages the ratchet |38 which is also fulcrummed on the upper shaft Ill, the ratchet |88 being fastened to the upper shaft will, therefore, turn the stop shafts 99 and |08 f of a revolution every time that the knife bar casting |45 makes a downward and an upward movement.

'I'he pawl lever |49 will turn in a clockwise direction by gravity whenever the crosshead |42 makes a downward stroke. I have given the example of thirty-seven cuts to completely cut up a given pile of paper which would require some mechanism operative after the thirty-seventh cut or while the thirty-seventh cut is being made to return the stop bars |00 and 98 to their original position. In order to accomplish this, the following mechanism is provided:

On the upper shaft is mounted a small pinion |31 having sixteen teeth, and this pinion meshes with a pinion |85 having thirty-two teeth, and this latter pinion meshes with a gear |34 having forty-eight teeth, and this pinion meshes with a gear |33 having sixty-four teeth. Cam |29 on thirty-two tooth gear |85 extends over 180; cam |29 on forty-eight tooth pinion |84 extends over 240; cam |21 on sixty-four tooth gear |38 extends over 270.

In other words, cam |29 attached to the thirtytwo tooth pinion |85 has a gap of 180, whereas the cam |28 attached to the forty-eight tooth pinion |34 has a gap of 120, and the cam |21 attached to the sixty-four tooth pinion |88 has a gap of 90. Now since we have used thirtyseven cuts as an example, we would use the cam |21 attached to the sixty-four tooth pinion |88.

For each index movement of the stop 99 and |80, these shafts will have made .1 revolution or 3.7 revolutions for thirty-seven cuts. Since the drive ratio between gear |81 on stop shaft |00 and gear |33 is four to one, cam |21 will have rotated 3/4 of a revolution during the iirst three revolutions of gear |81 which resulted from thirty cuts and .7 of the remaining quarter of a revolution during the remaining .7 of a revolution of gear |81 resulting from the last seven cuts.

The circular cam |21 which is fastened to the sixty-four tooth pinion |88 is contacted by a lever |25 on pin |09 which during the rst thirty indexing movements (the first three revolutions of gear |81 and the rst 94 revolution of gear |88) will have been in contact with the circular porvpawl |55 is pivoted tion of the cam 21 on the sixty-four tooth pinion |88; but beginning with the thirty-rst knife stroke, the lever |25 may drop into the gap which extends for 90 on the cam |21 on the sixty-four tooth gear |88.

On the lower shaft near its extremity is fastened the small drum |24 (Figure 1'1) and this drum is provided with ten slidable index pins I9. These pins have a circular groove ||8 in the middle, said groove serving for a ball ||1 under spring pressure from the spring I6 whereby these pins I |9 can be pushed inwardly and held in place by the ball 1. A second groove ||5 on the pin ||9 similarly serves for the purpose of holding said pin in its extended position. Springs ||5 and balls ||1 are positioned by the radial bores ||2 in drum |24.

When thirty-seven cuts are to be made, six pins 9 will be set by the operator in their protruding position, and the seventh, eighth, ninth, and tenth pins 9 will be in their retracted position. 'I'he lever |25 is pivoted on a pin |09 in the bracket |05 to engage cam |28. Lever |01 is pivoted on pin |0| in bracket |05 to contact cam |29. Lever |53 is pivoted on extension |00aof the upper shaft. The outer forked end of lever |58 carries the upper end of the vertical flat bar |54. A on a pin |59 also fast in the bracket |06, and one end of this pawl is connected to the at bar |54.

The vertical fiat bar |54 carries three pins |55, |51, |58 about equally spaced; these pins are in cooperating relation, respectively, with the three levers |01, |01a, |25. The arm |'55a of pawl |55 is contacted by the pins 9; and the flat bar |54 is prevented from dropping vertically by these pins ||9, but when the stop bars 99am! |00 are indexed for the thirty-seventh time and -as previously stated pin #1 of the pins ||9 in the drum |24 is in its retracted position, the pawl `|55 will now permit the flat bar |54 on the lever |53 to drop, whereby the lever |25 can now drop into the gap of the cam tooth pinion |33 and when lthis occurs, the pawl |55 will then turn out of engagement or will turn counterclockwise a suflicient amount so that the pawl |52 will contact the extending pin from the chain |32.

In other words, after the thirty-sixth cut has been made, the pin extending from the chain will be six pitches from its starting position, and then the pawl |52 comes in contact during the thirtyseventh up stroke of the cross head |42 with that extended pin on the chain and will then move the chain forward the remaining four pitches to bring the stop bar back to its In a similar manner, let us assume now that thirteen cuts will complete all of the cutting operations on a given pile of paper. I would then use the first cam |29 on the thirty-two tooth pinion |35 and push out only two pins ||9 on the drum |24 whereupon after the tenth knife stroke, the cam |29 on the thirty-two tooth pinion |35 would permit the pin |55 on bar |54 held up by lever |01 to drop provided the pawl |55 were not held out by one of the pinsv ||9 protruding from the drum |24, but since only two original position.

of such pins ||9 are protruding, then on the thircross head 42, the

teenth reciprocation of the pawl |55 can turn counterclockwise and the flat bar |54 can now drop because the lever |01 is now in the gap of the cam |29 on the thirty-two tooth pinion |35 and thereby the pawl' 52 can also turn counterclockwise so that its pushing end will be directly underneath the extended pin 21 on the sixty-foury 7 |35 on the chain |32. When the cross head |42 makes its thirteenth upward stroke, the pawl |52 will contact said protruding pin |35 on the chain |32 and will in .this case move it up eight pitches whereby it will return the stop bars 99 and |00 to their original position.

Assume now that we have twenty-five cuts to make in order to completely cut up a given pile of paper stock. I would then use the cam |28 on the forty-eight tooth pinion |34 and use the `lever |01a, and we would have four pins ||9 protruding from the drum |24 so that after the twentieth knife stroke, the lever |01a will be permitted to drop in the gap of the cam |28 on the forty-eight tooth pinion |34 and whenever the pawl |55 is permitted to turn in a counterclockwise direction due to the absence of the fifth pin ||9 winch is in its retracted position on the drum |24, which will then also permit the counterclockwise turning of the pawl |52, and this will bring the end of said pawl |52 directly for any pile up to ten; cam |29 is used for piles up to twenty; cam |28 is used for piles up to thirty; cam 21 is used for piles up to forty. Cams |29 and |28 may remain in position when cam |21 is used; but cams |21 and |28 must be removed to permit the use of cam |29. In the alternative, pins |55, |51, and |58 may be made removable or levers |01, |01a and |25 may be made removable.

The pawl |52 as previously described may be l in a first angular position where it contacts the pin |5| on the pawl lever |49 during the up stroke of the cross-head |42, or in a second angular position where it will contact one of the extended pins of the chain |32 during the up stroke of the cross-head |42.

A guide |50 is fastened to the righthand bracket |05 and the narrow strip on said guide will be against the face A of the pawl |52 when it is in the first angularV position, and the narrow strip of the guide |50 will run in the groove B of the pawl |52 when it is in the second angular position (Figures 17 and 18).

If, for any reason, the operator wishes to disconnect the indexing of the stop bars 99 and |00, he will lift the pawl |52 out of engagement with the ratchet wheel |38 and then it will not index on the upward or return stroke of crosshead |42. The knife may then simply go up and down without indexing the back gauge.

Power mechanism for actuating the back gaugel The motive power for moving the back gauge forward is derived from a constantly rotating motor 25. This motor drives at constant speed one member of a three-element planetary gear train. while a second element of the planetary gear train is driven at a minimum speed and will have this speed increased by 100%; the third element is the planetary gear carrier.

When the second element, i. e., gear rotates at its minimum speed, the planetary gear carrier will be rotating at its highest speed and when the second element has its sneed increased to a certain maximum, it will result in bringing the speed of the planetary gear carrier down to zero. This speed variation of the second element of the planetary transmission is accomplished by varying the diameter of the two interlocking V-belt pulleys actuated by a single belt and idler pulleys. Since the available motor speed is usually about 1750 R. P. M., this speed is reduced by means of V-belt and pulleys to about 900 R. P. M.

The pulley 2| is driven by means of a V- eelt 22 from the pulley 23 of motor 20. Pulley 2| has secured thereto a pinion 24 having thirty-.ive teeth. This pinion meshes with a compound gear 25 comprising concentric gear elements 26 and 21 having thirty-ve and twenty teeth, respectively, on shaft 28 (Figures 5 and 15). The twenty tooth pinion 21 of this compound gear 25 meshes with the fifty tooth gear 29 which is fastened by key 30 to a long sleeve 3| on the other end of which is mounted a gear 32 having forty-five teeth.

In other words, the thirty-five tooth pinion 24 which is integral with the pulley 2| rotates on the long sleeve 3| and drives the compound pinion 25 comprising gears 25 and 21, said compound pinion being free to turn on the ilxed stud 28 which is secured in the center section of the back gauge.

The forty-ve tooth gear 32, therefore, is the constant speedV member of the planetary gear train. Also freely rotating on the long sleeve 3| is the adjustable interlocking pulley 33 which interlocks with a similar V-belt cone pulley 34 on the V-belt pulley 2|. Also journalled on the long sleeve 3| is the pinion 35 and interlocking V-belt cone pulley 35 with which pinion 35 is integral. The interlocking cone pulley has a mating member 31. Pulleys 33 and 31 are mounted on ball bearing races 38 and 39 on pulley carrier 40 which is slidable on long sleeve 3|.

The planetary gear carrier 4| has mounted thereon the two planetary pinion shafts 42 and 43 on which are journalled the compound planetary gears 44 and 45. Pinions 45 on compound gears 44 and 45 each has eighteen teeth and meshes with the constant speed gear 32 which has forty-five teeth; and the planetary pinions 41 on compound gears 44 and 45 each has forty-two teeth and meshes with the pinion 35 on pulley 35 which has twenty-one teeth. The interlocking V-belt cone pulleys 33, 34 drive by means of the V-belt 48, the interlocking pair of cone pulleys 35 and 31.

This V-belt 48 is guided over idler pulleys 49 and 50 which are mounted on studs 5|, 52 held in brackets 53, 54. Bracket 54 is mounted on shaft 55 which passes through a long bore of the bracket 53. A spring 51 compressed between the collar 58 of shaft 55 and the top of bracket 53 maintains the V-belt 48 under tension. The belt tightening and guiding bracket 53 is supported by the vertical post 55.

The interlocking V-belt pulleys 31 and 33 have interposed between them the shifting yoke 50 which is an extension on both sides of the central sliding carrier or yoke 40.

The center section of the back gauge has mounted on it a bracket 5| which is provided with a bore for receiving the shaft 52. Shaft 62 protrudes on either end of the bracket 5|. On one end of shaft 52 is fastened the short shifting arm 53 and on the other end of the shaft 52 is fastened the long shifting arm 54. These two shifting arms 43 and 54 are slotted at 55, 30 to receive the trunnions 61, 68 of the shifting yoke 60 whereby the effective diameters of lthe two interlocking sets of V-belt cone pulleys can be changed by shifting the yoke 60 and thereby change the speed of the driven gear 36 while the speed of the driving gear 33 remains constant with the result that the speed of the planetary gear carrier 4| is affected thereby.

As previously mentioned, the stop` bars 99, each are provided with ten longitudinal splines |40 in which a series of stop blocks |25 can be fastened at any points required on the two stop bars 99 and |00. A long rectangular bar 10 is fastened between the two brackets |06 and on this rectangular bar is slidably mounted the carriage 1|. Carriage 1| is provided on brackets 12 and 13 with two retractable stop fingers; said fingers may be made to project so that they will come in contact with any one of the blocks |25 fastened in the stop bars 99 and |00.

In other words, when the upper stop bar |00 is used, the stop pin or nger 15 which is normally used for contacting the blocks |25 in the lower stop bar 99 is withdrawn and vice versa if the lower stop bar 99 is being used, the stop pin or finger 14 which normally coacts with the blocks |25 in the upper stop bar |00 is withdrawn.

The carriage 1| is also provided with brackets 16 and 11 (Figure 11). These brackets will form a retaining plate for the carriage 1| as it slides on the rectangular flat bar 10. The bracket 16 has a bore for receiving the threaded cable end 18 of cable 19, while the bracket 11 has a bore and a pin 8| for receiving the cable end 80. Cable end 80 has three notches 82 which can be used when the cable 19 has stretched beyond a certain amount and it becomes necessary to take it up after there is insumcient thread left on the cable end 18.

These cable ends 18 and 80 of cable 19 not being in the same plane will not interfere with each other.

The brackets |06 are each provided with lugs 84 for receiving the studs 85 of the cable idler pulleys 86. Near the center of the paper cutting machine and attached to the upper beam casting by vertical shaft 89 are two cable idler pulleys 81 and 88; and immediately behind the clamp of the paper cutting machine an additional idler 90 is mounted on a bracket 9| which is also fastened to the top beam casting of the paper cutting machine.

An additional cable idler pulley 92 is provided on a bracket 93 at the rear of the paper cutting machine table. Bracket 93 also has a large bore 94 (Figure 15) for the bearing for the back gauge driving shaft 95. Shaft 95 extends from the rear of the paper cutter table almost to the clamp of the paper cutting machine and has a long spline 96 over which the long sleeve 3| fits.

In other words, the driving power from the planetary gear carrier 4|, the latter having a key 91 which fits into the long spline of the shaft 95, transmits the driving power through the shaft 95 to the V-belt pulley |10 and by means of the V-belt |1| drives a similar pulley |12 on the end of the long lead screw |13 which passes through the collar |14 at the bottom of table |16 and threads in the nut |15 secured to back gauge support |11 for back gauge |18 on a long tongue |19 passing through slot guide |80 (Figure l5) in table |16 to the bottom side of the paper cutting machine table |16 and held to a close running it by means of the gib 8|,

The back gauge support 11 is secured by means of bolts to the back gauge |18 of the paper cutting machine so that when the pulley |12 on screw |13 turns in either direction, the back gauge of the paper cutting machine will move accordingly.

The cable 19 (bottom right portion of ,Figure 5 as well as Figures 15 and 16) passes through the clamp |90. Clamp |90 is provided with a pin |9| from which one end of the link |92 is suspended. The other end of the link |92 ts over a pin |93 which is carried by the long shifting lever 64. Thus, one side of the cable 19 extends from cable end 18 at the front of the machine over idler 86 on the left side, over idler pulley 88, then idler 90 to rear idler 92, and then to cable clamp |90 on the back gauge assembly.

The other end of the cable which ends at the cable end at the front of the machine extends over the right-hand idler pulley 86 and thence over the idler pulley 81 and from there (Figures 4, 15 and 16) over the idler pulley |94 supported by bracket |95 on hollow post 55 to the idler pulley |96 on the bracket |91, the latter being also mounted on the hollow tube 55. This hollow tube 55 has two drilled holes |91, |91 through which the cable 19 passes when going from idler pulley |94 to idler pulley |96. The cable then enters again the clamp piece |90.

Thus, the complete circuit for cable 19 is from end 18 at the front of the machine to left-hand idler 86, pulleys 88, 90, and 92 to clamp |90 on the back gauge; and from clamp |90, over idlersk |96, |94, 81 and right-hand idler 86 back to end 80 at the front of the machine.

When now one of the vstop fingers 14 or 15 in the bracket 1| makes contact with one of the stop blocks |25 on either of the shafts 99 or |00, it will stop the cable 19 from further movement. Because the cable 19 comes to rest, the clamp piece will also have come to rest; since clamp |90 is connected by means of the link |92 to pin |90 at the lower extremity of the longvshift arm 64, the lower end of arm 64 will also have come to rest.

The motor 20, however, through the drive outlines in connection with Figures 5 and 15 is still driving screw |13 to advance the back gauge. The shift yoke 60 is now brought into operation. The lower pin |93 will be the pivot point for the movement of the shift yoke 60 because the upper end of the shifting arm 64 is fastened to the shaft 62 which is carried in the bracket 6| of the center back gauge section; and shaft 62 is moving forward with the back gauge.

This forward motion of the shaft 62 causing arm 64 to pivot about lower pin |93 and thus moving trunnion 66 of shift yoke 60 forward will shift or disturb the relation between the interlocking V-belt cone pulleys 36-31 and 33-34 from the solid line positions of Figure 5 to the dotted line positions thereof; this will force V-belt 48 to run on a larger diameter of pulleys 36-31 which have been brought together and at the same time will cause the V-belt 48 to run on a smaller diameter of the interlocking cone pulleys 33-34 which have been separated.

The speed of driven gear 36 has now been increased. An increase in speed of gear 36 will result in a decrease in speed of the planetary gear carrier 4|. Therefore, continued movement of the shaft 62 to the left will continue to decrease the speed of the planetary gear carrier 4| until nally the back gauge will come to a stop. The back gauge is thus gradually stopped.

The operator will now make a cut operating the Knife |45 in any suitable manner. As previously described, the cross head |42 will be reciprocated downwardly and then upwardly and during this upward stroke will index the stop bars 90 and 1/m of a revolution.

When this occurs, the particular block |25 which was now contacted by the stop pin 14 or 15 in carriage 1I will move out of contact with this pin. The cable 19 is now free to move once more. The arm 04 which is released for movement when cable 10 is released by rotation of stop |25 out of the way of fingers 14 or 15 will be urged by the spring |90 to again shift the cone pulleys 31-33 to the right.

Spring |98 around post |99 bears upwardly against collar 200 attached to extension 20| of arm 202, which in turn is an extension of lever 04. Arms 64 and 202 form a bell crank lever secured to shaft B2.

This shift will again decrease the speed of the pinion pinion will result in an increase of speed of the planetary gear carrier 4| and bring the back gauge gradually to its maximum forward speed until the stop finger 14 or 15 on the carriage 1| will again come in contact with the next block of the stop bars 99 or |00. This will again arrest the motion of the cable and then the continued forward motion of the back gauge will again cause a shifting of the interlocked cone pulleys 31-33 and result in an increase in speed of the pinion 36 to cause a decrease in speed of the planetary gear carrier 4| until finally the planetary gear carrier 4| comes to a dead stop. A stop screw 200 (Figure 16) is provided on the back gauge to abut against the lower end of shift lever 64 at the dead stop position to prevent accidental movement of the position.

For the convenience of the operator, an indicating light 204 is provided which will teli him whether the back gauge has stopped at the correct location. For this purpose, two rectangular metal strips 204-205 are mounted on an insulating block 206 and fastened by means of screw-:s to a rib on the center section |11 of the back gauge. A link 201 is pivoted on the pin |93 which is carrled on the bottom end of the long shifting lever 64.

On the other extremity of this link 201 is mounted a roller 208. This roller is metallic and has a fiber insulated center mounted on the screw 220. Therefore, whenever the shifting lever 64 has come against the stop screw 203, roller 208 will have made electrical contact across the two rectangular plates 204-205, and these rectangular plates can be placed into an electric circuit with an indicating lamp 204, the roller 200 merely closing the electric circuit so that the indicating lamp will light when the back gauge has stopped at the correct position.

On completion of the series of steps of the back gauge, the motor may be reversed to drive the back gauge back to its initial position. To facilitate this return movement, the stop fingers 14 are beveled as seen in Figure 19 so that they may push back against the springs 2|! to clear the stops 2 0 as they move past.

In Figure 20 I have shown graphically the manner in which the combination of the variable speed drive and the gear train results in reduction of speed to zero as the back gauge approaches the pre-set point; the graph illustrating the result of the operation of levers 63-04 (Figure 16) to bring the mechanism of Figures 5 and 15 in a gradual halt.

36, and such decrease in speed of this back gauge beyond this The speed relation diagram, Figure 20. is constructed as follows:

1. Draw a horizontal line on which will be represented the speed of the third element or spider 4 I.

2. Draw two perpendicular lines to this horizontal line spaced a suitable distance apart.

3. Mark the intersection of the left perpendicular 0 and that of the right perpendicular 900 R. P. M.

4. On the left perpendicular the constant speed of the first planetary gear element (gear 32) is represented.

5. On the right perpendicular the variable speed of the second planetary gear element (gear is represented and marked 900 R. P. M.

6. Compute the speed and direction of rotation of spider 4I when the gear 32 is held stationary and gear 35 turns 900 R. P. M.

'1. Mark oi! on horizontal line, -225 R. P. M. to horizontal scale.

8. Draw a line from -225 R. P. M. on horizontal line to 900 R. P. M. on the right perpendicular line.

9. Draw a horizontal line parallel to first line drawn at a distance 360 R. P. M. to scale of right perpendicular.

10. Draw a line from -225 R. P. M. through the point of intersection of the 360 R. P. M. line of item 9 above with the left perpendicular and note its intersection produced with the right perpendicular.

11. This intersection will be at 1800 R. P. M. on the right perpendicular line, which must be the speed of gear 35 when gear 32 rotates 360 R. P. M. and when the spider 4| stands still.

In the foregoing I have described my invention solely in connection with specific illustrative embodiments thereof. Since many variations and modications of my invention will now be obvious to those skilled in the art, I prefer to be bound not by the specific disclosures herein contained but only by the appended claims.

I claim:

l. In apparatus including a gauge, means for advancing the gauge to a plurality of pre-selected successive positions; said means including an operating mechanism; an infinitely variable speed changer for said operating mechanism adapted to vary the output speed thereof from zero to a predetermined maximum; means operable on the speed changer to shift the output speed of the operating mechanism to the maximum on the occurrence of a predetermined condition and means responsive to the movement of the gauge to a predetermined position before a pre-selected position to operate the speed changer to shift the output speed of the operating mechanism gradually from the maximum speed toward zero speed; said last mentioned means bringing the 15 output speed of the operating mechanism to zero speed when the gauge reaches the pre-selected position.

2. In apparatus including a gauge, means for advancing the gauge to a plurality of pre-selected successive positions; a plurality of adjustable stops movable to positions corresponding to said pre-selected positions; said means including an operating mechanim; an infinitely variable speed changer for said operating mechanism adapted to vary the output speed thereof from zero to a predetermined maximum; a member movable with the gauge; a portion of said member being arranged to be halted by each stop in turn; said member being connected to the speed changer and being movable with respect to the gauge to shift the output speed of the operating mechanism between a maximum at one position of said member and zero at another position of said member; said member being positionable at the maximum speed position to cause said gauge to move; a portion of said member being halted by a stop at a predetermined position of the gauge before a pre-selected position; the said member thereafter moving with respect to said gauge to shift the output speed of the operating mechanism` gradually from the maximum speed to zero speed between the last-mentioned predetermined l position and the pre-selected position.

3. In apparatus including a gauge, means for advancing the gauge to a plurality of pre-selected successive positions; said means including an operating mechanism; an infinitely variable mechanical speed changer for said Operating mechanism adapted to vary the output Speed thereof from zero to a predetermined maximum; means operable on the speed changer to shift the output speed of the operating mechanism to the maximum on the occurrence of a predetermined condition and means responsive to the movement of the gauge to a predetermined position before a pre-selected position to operate the speed changer to shift the output speed of the operating mechanism gradually from the maximum speed toward zero speed; said last-mentioned means bringing the output speed of the operating mechanism to zero speed when the gauge reaches the pre-selected position.

4. In apparatus including a gauge, means for advancing the gauge to a plurality of pre-selected successive positions; a plurality of adjustable stops movable to positions corresponding to said pre-selected positions; said means including an operating mechanism; an infinitely variable mechanical speed changer for said operating mechanism adapted to vary the output speed thereof from zero to a predetermined maximum; a member movable with the gauge; a portion of said member being arranged to be halted by each stop in turn; said member being connected to the speed changer and being movable with respect to the gauge to shift the output speed of the operating mechanism between a maximum at one position of said member and zero at another position of said member; said member being positionable at the maximum speed position to cause said gauge to move; a portion of said member being halted by a stop at a predetermined position of the gauge before a pre-selected position; the said member thereafter moving with respect to said gauge to shift the output speed of the operating mechanism gradually from the maximum speed to zero speed between the last-mentioned predetermined position and the pre-selected position; means operable to move said stop from halting connection with said 14 member; said member being thereafter movable with respect to the gauge to shift the output speed of the operating mechanism from zero to the maximum.

5. In apparatus including a gauge, means for advancing the gauge to a plurality of pre-selected successive positions; transmission means in said advancing means having an infinitely variable output speed between zero speed and a maximum speed; means for shifting said transmission means toward maximum output speed; and means operable at a predetermined position of the gauge before a pre-selected position of the gauge to shift said transmission means toward zero output speed; said last-mentioned means causing said transmission means to reach zero .output speed at said pre-selected position.

6. In apparatus including a gauge, means for advancing the gauge to a plurality of pre-selected successive positions; transmission means in said advancing means having an infinitely variable output speed between zero speed and a maximum speed; means for shifting said transmission means toward maximum output speed; and means operable before the gauge reaches a preselected position to shift the transmission output speed toward zero.

7. In apparatus including a gauge, means for advancing the gauge to a plurality of pre-selected successive positions; transmission means in said advancing means having an infinitely variable output speed between zero speed and a maximum speed; means for shifting said transmission means toward maximum output speed; and means operable before the gauge reaches a preselected position to shift the transmission output speed toward zero; said transmission output speed reaching zero when the gauge reaches said pre-selected position.

8. In apparatus including a gauge, means for advancing the gauge to a plurality of pre-selected successive positions; transmission means in said advancing means having an infinitely variable output speed between zero speed and a maximum speed; control means for said transmission comprising a rocking lever movable between angular positions corresponding to maximum and zero output speed of said transmission; means actuated by the forward travel of the gauge when it reaches the forward limit of its motion at a Dre-selected position to turn the lever to zero output speed of the transmission.

9. In apparatus including a gauge, means for advancing the gauge to a plurality of pre-selected successive positions; transmission means in said advancing means having an infinitely variable output speed between zero speed and a maximum speed; control means for said transmission comprising a rocking lever movable between angular positions corresponding to maximum and zero output speed of said transmission; means actuated by the forward travel of the gauge when it reaches a predetermined position before the forward limit of its motion at a preselected position to initiate the movement of the rocking lever toward zero output speed of the transmission.

10. In apparatus including a gauge, means for advancing the gauge to a plurality of pre-selected successive positions; transmission means in said advancing means having an infinitely variable output speed between zero speed and a maximum speed; control means for said transmission comprising a rocking lever movable between angular positions corresponding to maximum and zero output speed of said transmission; means actuated by the forward travel of the gauge when it reaches a predetermined position before the forward limit of its motion at a pre-selected position to initiate the movement of the rocking lever toward zero output speed of the transmission; said rocking lever reaching zero output speed of the transmission when the gauge reaches said pre-selected position.

11. In apparatus including a gauge, means for advancing the gauge to a plurality of pre-selected successive positions; transmission means in said advancing means having an infinitely variable output speed between zero speed and a maximum speed; control means for said transmission comprising a rocking lever movable between angular positions corresponding to maximum and zero output speed of said transmission; means actuated by the forward travel of the gauge when it reaches a predetermined position before the forward limit of its motion at a preselected position to initiate the movement of the rocking lever toward zero output speed of the transmission; said rocking lever reaching zero output speed of the transmission when the gauge reaches said pre-selected position; said gauge being brought to a gradually decelerated halt at said pre-selected position.

12. In apparatus including a gauge, means for advancing the gauge to a plurality of preselected successive positions; transmission means in said advancing means having an infinitely variable output speed between zero speed and a maximum speed; control means for said transmission comprising a rocking lever movable between angular positions corresponding to maximum and zero output speed of said transmission; means actuated by the forward travel of the gauge when it reaches a predetermined position before the forward limit of its motion at a preselected position to initiate the movement of the rocking lever toward zero output speed of the transmission; said gauge being brought to a gradually decelerated halt at said pre-selected position.

13. In a cutting machine including a reciprocating knife and a back-gauge, means for stepping said back-gauge to a plurality of preselected successive positions; said means including operating mechanism driving said backgauge; means responsive to the completion of the movement of the knife to initiate said operating mechanism; a plurality of adjustable stops and a stop engaging member movable with said back-gauge; said operating mechanism including an infinitely variable mechanical speed changer operable to vary the output speed thereof from aero speed to a maximum; means responsive to the engagement of said stop engaging member with one of said stops to operate said speed changer through an infinite series of speed changes to bring the operating mechanism and the back-gauge to a gradual halt.

14. In a cutting machine including a reciprocating knife and a back-gauge, means for stepping said back-gauge to a plurality of preselected successive positions; said means including operating mechanism driving said backgauge; means responsive to the completion of the movement of the knife to initiate said operating mechanism; a plurality of adjustable stops and a stop engaging member movable with said back gauge; said operating mechanism including an infinitely variable speed changer operable to vary the output speed thereof from zero speed to a maximum; means responsive to the engagement of said stop engaging member with one of said stops to operate said speed changer through an infinite series of speed changes to bring the operating mechanism and the back-gauge to a gradual halt.

15. In a cutting machine including a reciprocating knife and a back-gauge, means for stepping said back-gauge to a plurality of preselected successive positions; said means including operating mechanism driving said backgauge; means responsive to the completion of the movement of the knife to initiate said operating mechanism; a plurality of adjustable stops and a stop engaging member movable with said back-gauge; means responsive to the engagement of said stop engaging member with one of said stops to decelerate said operating mechanism and said back gauge through an infinitely variable diminishing speed to a halt.

16. In a cutting machine including a reciprocating knife and a back-gauge, means for stepping said back-gauge to a plurality oi preselected successive positions; said means including operating mechanism driving said backgauge; means responsive to the completion of the movement of the knife to initiate said operating mechanism; a plurality of adjustable stops and a stop engaging member movable with said backgauge; means responsive to the engagement of said stop engaging member with one of said stops to halt said operating mechanism.

17. In a cutting machine including a reciprocating knife and a back-gauge, means for stepping said back-gauge to a plurality of preselected successive positions; said means including operating mechanism driving said backgauge; means responsive to the completion of the movement of the knife to initiate said operating mechanism; a plurality of adjustable stops and a stop engaging member movable with said back-gauge; means responsive to the engagement of said stop engaging member with one of said stops to decelerate said operating mechanism and said back gauge to a halt.

18. In a cutting machine including a reciprocating knife and a back-gauge, means for stepping said back-gauge to a plurality of preselected successive positions; said means including operating mechanism driving said backgauge; said operating mechanism including an infinitely variable speed changer operable to vary the output speed thereof from zero speed to a maximum; said operating mechanism and backgauge being halted during the operation of the knife; means responsive to the completion of the movement of the knife to vary the speed changer to bring the operating mechanism and the backguage into movement; a plurality of adjustable stops and a stop engaging member movable in response to movement of said back-gauge; means responsive to the engagement of said stop engaging member with one of said stops to operate said speed changer through an infinite series of speed changes to bring the operating mechanism and the back-gauge to a gradual halt.

19. In a cutting machine including a reciprocating knife and a back-gauge, means for stepping said back-gauge to a plurality of preselected successive positions; said means including operating mechanism driving said backgauge; said operating mechanism including an infinitely variable speed changer operable to vary the output speed thereof from zero speed to a maximum; said back-gauge being halted during back gauge; means for ing mechanism gradually to zero and to gradually halt the back-gauge at a predetermined position.

20. In a machine oi the character described, a back gauge. means -for advancing the back gauge step by step, said means comprising a transmission having an inilnitely variable speed between a maximum speed and zero speed, a rocking member operatively connected with said transmission having extreme angular positions corresponding with the maximum and zero speed positions of the transmission respectively and having an infinite series of intermediate positions corresponding with intermediate speeds of the transmission, and means actuated by the travel of the back gauge at the forward limit of its motion Ifor turning the rocking member through intermediate positions to the zero position.

21. In apparatus for advancing a gauge (to a plurality of pre-selected successive positions) transmission means having an innitely variable series of operative positions between a maximum speed and zero speed; control means for shifting said transmission through said variable series oi' operative positions to zero speed and to maximum speed; said control means being movable with said gauge and being operable in accordance with successive predetermined positions thereof related to said successive pre-selected positions.

22. In apparatus for advancing a gauge; transmission means having an ininitely variable series of operative positions between a maximum speed and zero speed; control means for shifting said transmission through said variable series of operative positions to zero speed and to maximum speed; said control means being movable with said gauge and being operable in accordance with the position of said gauge.

23. In apparatus of the character described, a back gauge; means for advancing the back gauge step by step to a plurality of successive preselected positions; a plurality oi' adjustable stop members individually settable to determine individual pre-selected positions; a stop engaging member movable in accordance with the movement of said back gauge and cooperating with successive stops to halt the back gauge advancing means successively in accordance with the position of successive stops; means operable after the halting of the back gauge by one stop to remove said stop from intercepting relation with said stop engaging member and to bring the next stop into the path of movement of said stop engaging member.

24. In apparatus of the character described, a advancing the back gauge step by step to a plurality of successive preselected positions; a plurality of adjustable stop members individually settable to determine individual pre-selected positions; a stop engaging member movable in accordance with the movement of said back gauge and cooperating with successive stops to halt the back gauge advancing means successively in accordance with the position of successive stops; means operable after the halting of the back gauge by one stop to remove means successively in accordance with the posi.

said stop yfrom intercepting relation with said stop engaging member and to bring the next stop into the path oi' movement ci said stop engaging member; said stop engaging member being linearly movable; said stops being moved successively into the line oi' movement of said stop engaging member.

25. In apparatus of the character described, a back gauge; means for advancing the back gauge step by step to a plurality of successive preselected positions; a plurality of adjustable stop members individually settable to determine individual pre-selected positions; a stop engaging member movable in accordance with the movement of said back gauge and cooperating with successive stops to halt the back gauge advancing tion of successive stops; means operable after the halting of the back gauge by one stop to remove said stop from intercepting relation with said stop engaging member and to bring the next stop into the path of movement of said stop engaging member; said stop engaging member being linearly movable, a stop mounting bar mounted parallel to the line of movement of said stop engaging member; the stops being mounted Von said bar; said bar being movable to bring the stops successively into the line of movement of said stop engaging member.

26. In apparatus of the character described, a back gauge; means for advancing the back gauge step by step to a plurality of successive preselected positions; a plurality of adjustable stop members individually settable to determine individual pre-selected positions; a stop engaging member movable in accordance with the movement of said back gauge and cooperating with successive stops to halt the back gauge advancing means successively in accordance with the position of successive stops; means operable after the halting oi the back gauge by one stop to remove said stop from intercepting relation with said stop engaging member and to bring the next stop into the path of movement of said stop engaging member; said stop engaging member being linearly movable, a stop mounting bar mounted parallel to the line of movement of said stop engaging member; the stops being mounted on said bar; at a plurality of angularly displaced positions around the longitudinal axis or said bar; said bar being movable angularly on its longitudinal axis to bring'the stops successively into the line of movement of said stop engaging member.

27. In apparatus of the character described, a back gauge; means for advancing the back gauge step by step to a plurality of successive preselected positions; a plurality of adjustable stop members individually settable to determine individual pre-selected positions; a stop engaging member movable in accordance with the movement of said back gauge and cooperating with successive stops to halt the back gauge advancing means successively in accordance with the position oi' successive stops; means operable after the halting of the back gauge by one stop to remove said stop from intercepting relation with said stop engaging member and to bring the next stop into the path of movement of said stop engaging member; said stop engaging member being linearly movable, a stop mounting bar mounted parallel to the line of movement of said stop engaging member; the stops being mounted on said bar at a plurality of angularly displaced positions around the longitudinal axis oi' said bar longitudinally displaced po- 

